Noiseless air-actuated turbine-type vibrator

ABSTRACT

This invention pertains to an air-actuated vibrator of the turbine-type in which the rotor and enclosing chamber is so contoured as to provide within the normal operating range a noise level which is below 85 db (Hertz). Preferably this noise level is about 72 db or less which is much below the tolerant level established as acceptable. The rotor is the only moving part in this vibrator and has its periphery formed with small transverse serrations such as gear-tooth, saw-tooth or similar profiles. The tooth profile is of such small size that the driven rotor which is peripherally driven by pressurized air within a normal supply range produces noise levels which are sufficiently low so that the operation of the vibrator is considered to be virtually silent.

[ Mar. 11, 1975 ABSTRACT NOISELESS AIR-ACTUATED TURBINE-TYPE VIBRATOR[76] Inventor:

g ir g 'X 3 i l 8 This invention pertains to an air-actuated vibrator ofen 898 the turbine-type in which the rotor and enclosin chamber is socontoured as to g provide within the normal operating range a noiselevel which is below 85 db (Hertz). Preferably this noise level is about72 db or less which is much below the tolerant level established asacceptable. The rotor is the only moving part in this vibrator and hasits periphery formed with small transverse serrations such asgear-tooth, saw-tooth or similar profiles. The tooth profile is of suchsmall size that the driven rotor which is peripherally driven bypressurized air within a normal supply range produces noise levels whichare sufficiently low so that the operation of the vibrator is consideredto be virtually Sllent.

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sum 3 r 4 MODEL I00 I I60 I90 250 PSI dB. RPM dB. RPM dB RPM CIB RPM dBRPM 30 55 6000 58 I500 6|.5 I800 63 I500 H0 70 H800 63.5 9900 64 600072.5 6I00 72 6000 PATENTED 1 I975 3,870,282 sum a ar 4 TOOTH SHAPE4OF.S.I. 5ORSJ. SOPSJ. 70RSJ. 80P5J. 9095.1. ON WHEEL I dB RPM dB RPM dBRPM dB RPM dB RPM dB RPM 48PITCH 78TEETH 56.5 3600 5Z5 4800 525 6000 586800 60 6900 63 7200 KNURLED 73 55 3800 55.5 4400 525 5400 58-5 620059.5 6600 63 7000 SAWTOOTH 32P'TCH 50TEETH55 6000 56 8500 5a 8700 58.58900 so 9000 as 10500 32PITCH SOTEETH 55 6800 55.5 7200 56.5 7200 577800 58.5 7800 59 B000 dB SAWTOOTH 32F RPM X I000 NOISELESS AIR-ACTUATEDTURBINE-TYPE VIBRATOR BACKGROUND OF THE INVENTION 1. Field of theInvention In accordance with the classification of art as established bythe U.S. Patent Office this invention is found in the general classentitled, Agitating (class 259) and the subclass therein entitled,miscellaneous (subclass l) which has been further identified in thissubclass as 1 R and Digest 43." The method of making a vibrationapparatus as in the embodiment shown is found in the general classentitled, Metal Working (Class 29) and the subclass therein ofimpellers" (subclass 156.8).

2. Description of the Prior Art Air turbines are not new and making therotor with an eccentric weight is also well known as seen in U.S. Pat.No. 3,074,151 to Kroeckel as issued on Jan. 22, 1963. Another patentusing the same general concept includes U.S. Pat. No. 2,875,988 toWysong as issued on Mar. 3, 1959. Other air driven vibrators alsogenerally used include ball-type vibrators as seen in U.S. Patents toPeterson, No. 2,793,009 as issued on May 21, 1957 and No. 2,917,290 asissued on Dec. 15, 1959. In the above apparatus-as well as others knownto the applicant the noise levels exceed the tolerance levels forcontinuous duty operation (i.e., 85 db) as established by the FederalOccupational Safety and Health Act of 1970.

The turbine-type pneumatic vibrator of this invention as reduced topractice and extensively tested and used in commercial installations hasoperated substantially continuously for weeks at noise levels below theestablished 85 db and many units of smaller size have operated at levelsof 60 to 70 db. This, of course, falls well within the safety limits ofthe federal standard. In sharp contrast to this quiet vibrator is theball-and-race vibrator now and for the past several years in extensiveuse. This ball-and-race vibrator is shown and described in U.S. Pat. No.2,793,009 as issued on May 21, 1957 and U.S. Pat. No. 2,917,290 asissued on Dec. 15, 1959 both to Peterson. The noise level usually foundin the installations of these ball-and-race vibrators is often in excessof 100 db. This noise level for periods of eight or more hours, ofcourse, is unacceptable.

In the present invention the size of the rotor, the number and depth ofteeth used therewith and the normal operating range of air pressure usedto drive the vibrator are closely related factors. The air turbinevibrator of this invention uses a close limit control of these factorsto successfully meet or exceed the requirements for a quiet operation ofthe vibration apparatus.

SUMMARY OF THE INVENTION The present invention may be summarized atleast in part with reference to its objects.

It is an object of this invention to provide, and it does provide, anair-actuated turbine-type vibrator in which the eccentrically weightedrotor has its periphery formed with a regular pattern and spacing ofsmall tooth forms. These tooth forms of a determined size andconfiguration commensurate with the size of the rotor.

It is a further object of this invention to provide, and it doesprovide, an air-actuated turbine-type vibrator in which the air inlet isof a size which is proportioned as to the diameter of the rotor. Theoutlet is also proportioned as to the diameter of the rotor. The ratioof the inlet to the outlet diameter of the smaller diameter vibrators isabout 40 percent of the outlet diameter whereas in the large diameterrotors the ratio of the inlet to the outlet is about 50 percent.

The air-actuated turbine-type vibrator of this invention as reduced topractice ranges from a rotor diameter of 1% inches to a diameter of5inches and the number of teeth carried by the rotor ranges from 50 toI00 teeth. The groove depth of the teeth on the various diameter rotorsranges from one thirty-second to onequarter of an inch depending uponthe diameter of the wheel. The air turbine of this invention includes astandard circumferential chamber in which the inlet and the outlet aredisposed on diametrically opposite sides. In the various size units theinlet and outlet diameters vary. The threaded portion of the inletterminates at about one-eighth to five-sixteenths of an inch dependingon size of the unit. The unthreaded portion creates a venturi actionprior to the inlet entering the peripheral path of the turbine Wheel.The inlet of the silent turbine is of a smaller diameter than is theoutlet. The turbine has an eccentric weighted rotor and the eccentricweight is selected as to the amount of vibratory force to be exerted.The teeth are formed on the periphery and are generally parallel to theaxis of the rotor and in many instances are gear-like in form. Thenumber-of teeth on the rotor is carefully calculated and in actual testsprovide the lowest db noise level achievement while providing a highrpm. output. The air-actuated turbine-type vibrator is contemplated tooperate at air pressure ranging from 30 to 110 p.s.i.

In addition to the above summary the following disclosure is detailed toinsure adequacy and aid in understanding of the invention. Thisdisclosure, however, is not intended to prejudice that purpose of apatent which is to cover each new inventive concept therein no matterhow it may later be disguised by variations in form or additions offurther improvements. For this reason there has been chosen a specificembodiment of the noiseless, air-actuated turbine-type vibrator asadapted for use with inlet air pressure of 30 to l 10 p.s.i. and showinga preferred means for the construction of the turbine chamber and thetooth profile formed on the periphery of the rotor.

This specific embodiment has been chosen for the purposes ofillustration and description as shown in the accompanying drawingswherein:

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 represents an explodedisometric view showing in general the constructional relationship of thevarious components which provide the air turbine vibrator of thisinvention;

FIG. 2 represents a partly sectional and partly diagrammatic side viewof the housing as used for the air turbine and showing in particular therelationship of the inlet and the outlet of a preferred housingarrangement of the air turbine;

FIG.-3 represents a chart showing the noise level changes provided byvarious inlet diameters of the smaller diameter vibrator. This chartshows the resulting decibel level and the r.p.m.s derived from either 60p.s.i. or p.s.i. inlet pressures. The inlet size diameter holes shownare used with a h-inch outlet diameter hole;

FIG. 4 represents a chart in accordance with table FIG. 3 and showingthe relationship of the noise level in dbs where the inlet hole diameteris varied while the outlet hole remains the same and with the same wheeloperating at two different inlet pressures, one at 60 p.s.i. and theother at 90 p.s.i.;

FIG. 5 represents a chart showing in graph form the relative db levelsand the increase or decrease in r.p.m.s resulting from changes in inletdiameter to a fixed outlet diameter, the information derived from chartFIG. 3;

FIG. 6 represents a tabulation or chart showing the derived r.p.m.s ofthe rotors of five different models. The inlet pressures increasing from30 to 110 p.s.i. The noise and r.p.m.s are noted for each of the fivemodels;

FIG. 7 represents a graph showing in graph form the chart information ofFIG. 6;

FIG. 8 represents a chart in which a rotor of 1% inches in diameter andmade with four different surface forms is compared as to r.p.m.s and thenoise level where the inlet pressures vary from 40 to 90 p.s.i., and

FIG. 9 represents a graph of the chart of FIG. 8 and demonstrates thatwhen about 90 percent of the absolute maximum r.p.m.s is reached thatthe least little increase in speed causes a high rise in the noiselevel.

In the following description and in the claims various details will beidentified by specific means for convenience; these names, however, areintended to be generic in their application. Corresponding referencecharacters refer to like members throughout the figures showing theconstruction of the turbine-type vibrator and in the charts and graphsused therewith.

The drawings and charts accompanying, and forming part of, thisspecification discloses certain details of construction for the purposeof explanation of the invention, but it should be understood thatstructural details may be modified in various respects without departurefrom the concept and principles of the invention and that theturbine-type vibrator may be incorporated in other structural forms thanshown.

DESCRIPTION OF THE PREFERRED EMBODIMENT Referring now in particular tothe drawings there is shown in FIG. 1 an isometric exploded view of thepreferred construction of the air turbine vibrator of this invention.This vibrator includes a housing generally designated as 10 and having abase adapted for mounting onto a flat surface. This base includes legportions 12 and 14 and above and between these portions is provided achamber portion 16 which is circular in configuration and of adetermined depth. This chamber has formed outwardly and on the near sidean outer larger circular recess 18 adapted to receive and retain adisclike end 20, which has mounted to it an axle 22. This axle includesan unthreaded portion 23 and at its left or distal end the axle isthreaded at 24 to receive and be retained by a nut 25. A back wall 26fixedly mounted in a recess in the housing closes off the rear portionof the chamber area 16. This back wall is formed with a hole 28providing a passage therethrough for the axle member 22.

Adapted for mounting on the axle 22 is a rotor generally designated as30. This rotor includes a ball bearing 32 which provides theantifriction bearing portion around which the rotor is driven. Aroundthis ball bearing 32 is a rotor portion 34 which has formed on the outerperiphery thereof teeth 36 whose size and spacing is essential in thequiet operation of the turbine. Between the bearing 32 and the outertooth portion 36 there is mounted in the rotor portion 34 heavierelements in the form of dowels or rods and generally identified as 38.These heavier elements may be of steel, sintered heavy metal, lead orthe like. These rods are mounted as by a press fit or by threadedretention into previously prepared holes in the rotor which is generallya die casting or aluminum. It is to be noted that the rotor need not belimited to metal as plastic may also be used. Since the air being fedinto the turbine often carries impurities with it in the form of rust,scale or dust the use of a plastic for the rotor may or may not befeasible depending upon the environment in which it is used. However, itis to be contemplated that the scope of this invention includes the useof plastics and the like for both the rotor and the housing.

Referring now to FIG. 2 there is depicted the preferred housingconstruction for guiding pressurized air to and from the chamber portion16. An inlet 40 has a threaded portion for mounting a threaded nippletherein. This thread is of a selected size and a like thread is providedin outlet 42. From chamber 16 the outlet has a drilled hole 43 which hasa diameter which is generally one-quarter of an inch or more. The inlet40 has the smooth reduced diameter 44 leading from the threaded portionto chamber 16 sized so as to provide a jet force with this reduceddiameter concentrating the incoming air as an impinging force on theteeth of the rotor. This short length 44 is about one-eighth tofive-sixteenths of an inch in length depending on the size of rotor andchamber. The diameter of section 44 is sized between about one-tenth toone-quarter inch according to various charts to be hereinafterdescribed.

Assembly of the Vibrating Turbine of this Invention The chamber 16 is ofa determined size which, as reduced to practice, is substantially thediameter of the rotor and may be from 1% inches to 5 inches. The weights38 placed in the rotor portion 34 may be light, medium or heavydepending upon the effective vibratory force exerted at the desiredoperating conditions of the unit. The ball bearing 32 is assembled inthe rotor 34 as a press fit in a bore formed therein. This assembly 30is then pressed on a snug fit on the smooth shank portion 23 of shaft 22after which the disc end 20 and the shaft mounted rotor are then pushedinto bore 16 of the housing 10. The periphery of the tooth portion 36provides a clearance of a few thousandths of an inch to one-sixteenth ofan inch between the outer periphery of the teeth and the inner surfaceof bore 16. The threaded end portion 24 of axle 22 is passed through thehole 28 and with nut 25 end 20 is drawn into recess 18 and when the nuthas been tightened the unit is assembled.

The effectiveness of this vibrator as far as operating at or below asafe noise level results from a careful forming of the teeth portion 36in the manner of straight-sided or slightly crowned tooth form. Therelationship of this toothform and the pressurized air fed through theinlet portion 44 of the inlet is selected so that the vibrator willoperate at maximum r.p.m.s with a noise level below 85 dbs andpreferably in the range of 65 to dbs which is less than the establishedlevel permitted where continuous presence of workmen in or around thesevibrators may occur without damage to their hearing.

As reduced to practice, and as seen in the following charts and graphsthe effective r.p.m.s of the rotor while maintaining the low level ofnoise is dependent on tooth size, inlet size and outlet size.

Chart of FIG. 3

In chart 3, the model 130 noted in later charts has a rotor which is 1%inches in diameter. The inlet hole identified as 44 is shown withvarying sizes while a onequarter inch diameter outlet hole is used forall these tests. A fixed number of teeth, as for example 50, and formedas a 32 diametral pitch gear is provided on this rotor. Inlet air at 60and 90 p.s.i. is fed in through the inlet whose hole diameter 44 isvaried from 0.059 to 0.226 inch in diameter. As noted in this chart thepreferred inlet diameter with the lowest sound level is found at 0.116inch hole diameter. This diameter results in a 61 db noise level at7,200 r.p.m. and with an increase of pressure from 60 p.s.i. to 90p.s.i. the db level goes up to 63 db at 2 foot on an A-scale. The rotorspeed of 7,800 r.p.m. at this diameter is substantially close to themaximum. Because of the effective r.p.m.s and the noise levels achievedthe inlet hole standard for this 1% diameter unit is one hundredten-thousandths of an inch. An effective inlet may vary from onehundred-one to one hundred thirty-six-thousandths of an inch indiameter. The inlet selected which has one hundred ten-thousandths inchdiameter has a noise level of 62 db at 7,600 r.p.m. and 60 pounds inletpressure and 62% noise level db at 8,000 r. p.m. and 90 pounds.

Chart of FIG. 3 and Graphs of FIGS. 4 and 5 Referring next to the chartof FIG. 3 and the graphs of FIGS. 4 and 5 there is depicted theimportance of the inlet size ofportion 44 to the fixed outlet size 43.Measurement of a vibrator was made of a rotor having 1% inches indiameter and having 50 teeth corresponding generally, if not exactly, toa 32 diametral pitch gear form. The inlet hole diameter varies from aminimum of fifty-nine-thousandths of an inch in diameter to a maximum oftwo hundred twenty-six-thousandths of an inch in diameter. The outletdiameter is fixed at onequarter inch diameter. As seen in the chart andthe graphs the speed in r.p.m.s increases from a low of 3,600 r.p.m.s atboth extremes of inlet diameter to the maximum r.p.m.s developed at onehundred tenthousandths of an inch in diameter. The noise level at thisstandard size is about 62 dbs at both 60 and 90 p.s.i. inlet pressureand at the same time the r.p.m.s are also at or near their maximum atthis diameter inlet.

FIG. 5 represents a graph of the noise level changes resulting from thechange in inlet openings as noted in the chart of FIG. 3. The minimumnoise levels are recorded when the inlet diameters are at one hundredtenand one hundred sixteen-thousandths inch in diameter. It is to benoted that where the inlet diameter approaches the size of the outletthat the r.p.m.s drop drastically while the noise level increases agreat deal. When the inlet diameter exceeds the outlet diameter the unitstalls.

Chart of FIG. 6 and Graph of FIG. 7

Referring next to the chart of FIG. 6 and the graph of FIG. 7 there isshown information and the relationship pertaining to the performance atvarious inlet pressures of five of the models which have their rotorsprovided with teeth in size and number designed to operate at optimumefficiency as to r.p.m.s of the rotor and the noise levels. Model No.100, for example, has a rotor with 57 teeth with a tooth form of 48diametral pitch. Line A" on the graph of FIG. 7 applies to the noiselevel versus the r.p.m.s of both Model and Model 130. This line isnearly a straight line. The line 8" re lates to the performanceoftheModel the line C" to Model and the line D" to Model 250.

As below noted the rotor diameter and tooth size gets progressivelylarger as the rotor size increases. As noted in both FIGS. 6 and 7 thelower decibel noise levels are desirable and'are achieved and in none ofthe models is the government standard maximum of 85 db approached orexceeded.

The models above noted and other in the series have preferred inlet andoutlet sizes to produce r.p.m.s which are nearly at the peak availablewhile the noise level is at or near the minimum. As noted below thepreferred inlet and outlet sizes and the tooth profile for the severalsizes are:

Standard Vibrator Design It is important to note that the inlet sizerelates to both rotor diameter and tooth size until the rotors using 24diametral pitch gear tooth sizes is reached. Even at the largest rotorsizes the ratio of the inlet to the outlet is about 50 percent. Thecareful relationship of tooth size and inlet and outlet size asestablished for use in these successful vibrators operate at noiselevels below 75 db at l and 2 feet.

Chart of FIG. 8 and Graph of FIG. 9

Having determined an effective design for a rotor of 1% inches indiameter the efficiency of the tooth shape used on the rotor wasanalyzed. Rotors with very fine teeth, with a knurled surface, with asaw-tooth form and with a standard gear-like tooth form were tested. Inthe chart of FIG. 8, all rotors were 1% inches in diameter. A rotorhaving a very fine gear-tooth form was provided with a 48 diametralpitch gear-tooth form and had 78 teeth. The noise level in dbs was justslightly higher than the 32 pitch model (selected as standard) seen inthe fourth line. The 32 diametral pitch rotor is formed with 50 teethand the r.p.m.s at 40 p.s.i. inlet pressure is 6,800. At 90 p.s.i. inletpressure the noise level in dbs is at a very satisfactory 59 whilerotating at 8,000 r.p.m.

In line three of FIG. 8 a saw-tooth formcorresponding somewhat to thetooth form seen in conventional turbines was provided on the turbinerotor and was made with 32 pitch and 50 teeth. Although the r.p.m.efficiency increased so also did the noise level in dbs and at 90 p.s.i.inlet pressure this level moved above 65 dbs. In line two, a rotorhaving its periphery formed with a coarse knurl with about 73 knurlsformed on the periphery had such a low r.p.m. output that it wasrejected as unacceptable even though the noise level was marginallyacceptable.

It is acknowledged that the r.p.m.s of the 32 diametral pitch rotorcould be greatly increased by forming the teeth as a saw-tooth, however,the saw-tooth rotor having a 32 pitch and 50 teeth disposed upon theperiphery at 40 p.s.i. derived r.p.m.s were slightly less than thestandard rotor while the noise level was exactly the same as thevibrator having the standard recommended rotor. With an increase inp.s.i. to 50 the r.p.m.s drastically jumped and the noise level moved to56 db. With 60 p.s.i. often and commonly used in vibrating systems, thenoise level moved to 58 db and the r.p.m.s increased to 8,700. At 70p.s.i. the noise level increased to 58% dbs which is well within theacceptable noise limit and at 70 p.s.i. the r.p.m.s go up to 8,900. Withthe inlet pressure increased to 80 p.s.i. the noise moved to about 60 dband the r.p.m.s increased to 9,000. At an inlet pressure of 90 p.s.i.the noise level moved to 66 db which is above the noise level of the 32pitch rotor ofline four and at the same time the r.p.m.s moved up to10,500.

Note that as seen on the chart of FIG. 8 and as represented on the graphof FIG. 9 that with 100 p.s.i. inlet pressure and the resultingincreased r.p.m.s cause the saw-tooth form and the 48 pitch wheel tooperate at noise levels in excess of 60 db. Since most air pressuresupply systems have 100 or more p.s.i. pressure available this must beconsidered when one is furnishing a quiet vibrator.

As of filing this application the noise level acceptable for 8 hourexposure is 85 db. This level is likely to be reduced in the near futureto 75 or 80 db. Assuming when the input diameter is from 30 to 55percent of the output diameter the number of teeth usable on a givenrotor is shown in the chart below. These teeth enable the vibrator tooperate at less than the 85 db limit.

Rotor Diameter Teeth 1% to 1% inches 40 to 80 1% to 2% inches 45 to 802% to 3% inches 45 to 85 3% to 5 inches 60 to l teeth Within theseranges the noise level is below 85 db. An appreciably lower noise levelthan this maximum is found when using the standard vibrator design abovenoted. The teeth configurations to maintain these low levels must berelatively alike and evenly spaced.

Terms apply to the position in which the turbine-type vibrator may beconstructed or used.

While a particular embodiment of this vibrator has been shown anddescribed it is to be understood the invention is not limited theretosince modifications may be made within the scope of the accompanyingclaims and protection is sought to the broadest extent the prior artallows.

What is claimed is:

1. A relatively silent, compressed gas-actuated, turbine-type vibratorhaving a rotor of not less than 1% inches and not more than 5% inchesdiameter and within a speed range of 6,000 to 10,000 rpms having a noiselevel not greater than decibels hz., the vibrator including: (a) asubstantially closed housing having a cylindrical chamber therein; (b) adynamically unbalanced rotor freely rotatable in the cylindrical bore ofthe chamber, the diameter and length of the rotor being established sothat not less than one thirty-second of an inch clearance is providedbetween the rotor and ends and bore of the chamber, the rotor having aplurality of tooth-like configurations formed on its outer periphery,the tooth-like configuration further having a depth which corresponds toa distance not exceeding 7 percent and not less than 1% percent of thediameter of the rotor; (c) an air outlet formed in the housing andextending from the rotor chamber to the outside of the housing, and (d)an air inlet formed in the housing and extending from the outside of thehousing to the rotor chamber, the air inlet arranged to direct theincoming pressurized air tangentially against the teeth of the mountedrotor and with the tooth like configurations so formed that in a planenormal to the axis of the rotor the face of the tooth like configurationagainst which the incoming air impinges defines an angle of intersectionwith the theoretical radial line of said rotor, said defined angle beingas little as 0 and as great as 30 as measured from said point ofintersection and inclined in such a direction that the circumferentialthickness of the tooth like configurations tends to decrease as theradial distance from the axis increases and with the tooth-likeconfiguration so formed that in a plane normal to the axis of the rotorthe face of the tooth-like configuration against which the incoming airimpinges defining an angle of intersection with a theoretical radialline of said rotor, said defined angle being as little as zero and asgreat as 30 as measured from said point of intersection and inclined insuch a direction that the circumferential thickness of the tooth-likeconfigurations tend to decrease as the radial distance from the axisincreases, the cross-sectional area of the inlet being 30 to 55 percentof the area of the outlet diameter.

2. A turbine-type vibrator as in claim 1 in which the rotor is providedwith gear-like teeth ranging in size from 48 to 24 diametral pitch onrotors whose outer diameters range from 1% inches to 5 inches.

3. A turbine-type vibrator as in claim 1 in which the length of thecontrolling inlet size is between oneeighth and five-sixteenths inch andthe diameter of the inlet is between one-tenth and one-quarter inch.

4. A turbine-type vibrator as in claim 1 in which at least one end ofthe chamber is closed by a disc and an axle on which the rotor ismounted is secured thereto, the disc adapted to snugly engage matingpositioning means formed at the opening and in which the other chamberend wall has an aperture sized to receive and retain the axle which ispassed therethrough and by a fastening means the axle and attached discis tightly drawn into a closing condition of the chamber.

5. A turbine-type vibrator as in claim 4 in which the rotor is carriedon a ball bearing mounted on the axle which is nonrotating whenassembled for use.

6. A turbine-type vibrator as in claim 1 in which rotors of 1%. inchesin diameter to and including 3 /2 inches in diameter have not less than40 teeth and more than 80 teeth, and rotors of 3% inches in diameter toand including 5 inches in diameter have not less than 60 teeth and morethan 120 teeth.

7. A turbine-type vibrator as in claim 1 in which the teeth on the rotorare arranged to lay in a plane passing through the axis of the rotor.

8. A turbine-type vibrator as in claim 1 in which the outlet and theinlet from and to the rotor chamber are each connected to a pipe tapopening formed in the housing.

9. A turbine-type vibrator as in claim 1 in which the housing isprovided with a pair ofleg portions providing means for securing theassembled vibrator to a device to be vibrated.

10. A turbine-type vibrator as in claim 1 in which a vibrator having arotor of 1% inches diameter has an inlet diameter of one hundrednine-thousandths inch and an outlet diameter of one-quarter inch.

11. A turbine-type vibrator as in claim in which the rotor of 1% inchesdiameter has its tooth profile as 48 diametral pitch or coarser.

12. A turbine-type vibrator as in claim 1 in which a vibrator having arotor of 1% inches diameter has an inlet diameter of one hundredsixteen-thousandths and an outlet diameter of one-quarter inch.

13. A turbine-type vibrator as in claim 12 in which the rotor of 1%inches diameter has its tooth profile as 32 diametral pitch or coarser.

14. A turbine-type vibrator as in claim 1 in which a vibrator having arotor of 1% inches diameter has an inlet diameter of one hundredsixteen-thousandths and an outlet diameter of one-quarter inch.

15. A turbine-type vibrator as in claim 14 in which the rotor of 178inches diameter has its tooth profile as 32 diametral pitch or coarser.

16. A turbine-type vibrator as in claim 1 in which a vibrator having arotor of 2 inches diameter has an inlet diameter of one hundredsixteen-thousandths and an outlet diameter of five-sixteenths inch.

17. A turbine-type vibrator as in claim 1 in which the rotor of 2 inchesdiameter has its tooth profile as 32 diametral pitch or coarser.

18. A turbine-type vibrator as in claim 1 in which a vibrator having arotor of 2% inches diameter has an inlet diameter of one hundredsixteen-thousandths and an outlet diameter of five-sixteenths inch.

19. A turbine-type vibrator as in claim 18 in which the rotor of 2%.inches diameter has its tooth profile as 32 diametral pitch or coarser.

20. A turbine-type vibrator as in claim 1 in which a vibrator having arotor of 2% inches diameter has an inlet diameter of one hundredtwenty-five-thousandths and an outlet diameter of three hundredninety-sixthousandths inch.

21. A turbine-type vibrator as in claim 20 in which the rotor of 2%inches diameter has its tooth profile as 24 diametral pitch or coarser.

22. A turbine-type vibrator as in claim 1 in which a vibrator having arotor of 3 /2 inches diameter has an inlet diameter of one hundredfifty-six-thousandths and an outlet diameter of three hundred ninety-sixthousandths inch.

23. A turbine-type vibrator as in claim 22 in which the rotor of 3 /2inches diameter has its tooth profile as 24 diametral pitch or coarser.

24. A turbine-type vibrator as in claim 1 in which a vibrator having arotor of 5 inches diameter has an inlet diameter of two hundredtwenty-thousandths and an outlet diameter of twenty-seven sixty-fourthsinch.

25. A turbine-type vibrator as in claim 24 in which the rotor of 5inches has its tooth profile as 24 diametral pitch or coarser.

P0405) UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent3,870,282 Dated March 11th, 1975 Inventor( Theodore Wadensten It iscertified that error appears in the above-identified patent and thatsaid Letters Patent are hereby corrected as shovm below:

Change inventor's address to read P,O, Box 8, Stilson Road, Wyoming,Rhode Island 02898 A change of address was filed with the Final Form.

Signed and sealed this 6th day of May 1975.

(SEAL) Attest:

C. MARSHALL DANN RUTH C. MASON Commissioner of Patents Attesting Officerand Trademarks

1. A relatively silent, compressed gas-actuated, turbine-type vibratorhaving a rotor of not less than 1 1/4 inches and not more than 5 1/2inches diameter and within a speed range of 6, 000 to 10,000 rpms havinga noise level not greater than 85 decibels hz., the vibrator including:(a) a substantially closed housing having a cylindrical chamber therein;(b) a dynamically unbalanced rotor freely rotatable in the cylindricalbore of the chamber, the diameter and length of the rotor beingestablished so that not less than one thirty-second of an inch clearanceis provided between the rotor and ends and bore of the chamber, therotor having a plurality of tooth-like configurations formed on itsouter periphery, the tooth-like configuration further having a depthwhich corresponds to a distance not exceeding 7 percent and not lessthan 1 1/2 percent of the diameter of the rotor; (c) an air outletformed in the housing and extending from the rotor chamber to theoutside of the housing, and (d) an air inlet formed in the housing andextending from the outside of the housing to the rotor chamber, the airinlet arranged to direct the incoming pressurized air tangentiallyagainst the teeth of the mounted rotor and with the tooth likeconfigurations so formed that in a plane normal to the axis of the rotorthe face of the tooth like configuration against which the incoming airimpinges defines an angle of intersection with the theoretical radialline of said rotor, said defined angle being as little as 0* and asgreat as 30* as measured from said point of intersection and inclined insuch a direction that the circumferential thickness of the tooth likeconfigurations tends to decrease as the radial dIstance from the axisincreases and with the tooth-like configuration so formed that in aplane normal to the axis of the rotor the face of the tooth-likeconfiguration against which the incoming air impinges defining an angleof intersection with a theoretical radial line of said rotor, saiddefined angle being as little as zero and as great as 30* as measuredfrom said point of intersection and inclined in such a direction thatthe circumferential thickness of the tooth-like configurations tend todecrease as the radial distance from the axis increases, thecross-sectional area of the inlet being 30 to 55 percent of the area ofthe outlet diameter.
 1. A relatively silent, compressed gas-actuated,turbine-type vibrator having a rotor of not less than 1 1/4 inches andnot more than 5 1/2 inches diameter and within a speed range of 6,000 to10,000 rpms having a noise level not greater than 85 decibels hz., thevibrator including: (a) a substantially closed housing having acylindrical chamber therein; (b) a dynamically unbalanced rotor freelyrotatable in the cylindrical bore of the chamber, the diameter andlength of the rotor being established so that not less than onethirty-second of an inch clearance is provided between the rotor andends and bore of the chamber, the rotor having a plurality of tooth-likeconfigurations formed on its outer periphery, the tooth-likeconfiguration further having a depth which corresponds to a distance notexceeding 7 percent and not less than 1 1/2 percent of the diameter ofthe rotor; (c) an air outlet formed in the housing and extending fromthe rotor chamber to the outside of the housing, and (d) an air inletformed in the housing and extending from the outside of the housing tothe rotor chamber, the air inlet arranged to direct the incomingpressurized air tangentially against the teeth of the mounted rotor andwith the tooth like configurations so formed that in a plane normal tothe axis of the rotor the face of the tooth like configuration againstwhich the incoming air impinges defines an angle of intersection withthe theoretical radial line of said rotor, said defined angle being aslittle as 0* and as great as 30* as measured from said point ofintersection and inclined in such a direction that the circumferentialthickness of the tooth like configurations tends to decrease as theradial dIstance from the axis increases and with the tooth-likeconfiguration so formed that in a plane normal to the axis of the rotorthe face of the tooth-like configuration against which the incoming airimpinges defining an angle of intersection with a theoretical radialline of said rotor, said defined angle being as little as zero and asgreat as 30* as measured from said point of intersection and inclined insuch a direction that the circumferential thickness of the toothlikeconfigurations tend to decrease as the radial distance from the axisincreases, the cross-sectional area of the inlet being 30 to 55 percentof the area of the outlet diameter.
 2. A turbine-type vibrator as inclaim 1 in which the rotor is provided with gear-like teeth ranging insize from 48 to 24 diametral pitch on rotors whose outer diameters rangefrom 1 3/8 inches to 5 inches.
 3. A turbine-type vibrator as in claim 1in which the length of the controlling inlet size is between one-eighthand five-sixteenths inch and the diameter of the inlet is betweenone-tenth and one-quarter inch.
 4. A turbine-type vibrator as in claim 1in which at least one end of the chamber is closed by a disc and an axleon which the rotor is mounted is secured thereto, the disc adapted tosnugly engage mating positioning means formed at the opening and inwhich the other chamber end wall has an aperture sized to receive andretain the axle which is passed therethrough and by a fastening meansthe axle and attached disc is tightly drawn into a closing condition ofthe chamber.
 5. A turbine-type vibrator as in claim 4 in which the rotoris carried on a ball bearing mounted on the axle which is nonrotatingwhen assembled for use.
 6. A turbine-type vibrator as in claim 1 inwhich rotors of 1 1/4 inches in diameter to and including 3 1/2 inchesin diameter have not less than 40 teeth and more than 80 teeth, androtors of 3 3/4 inches in diameter to and including 5 inches in diameterhave not less than 60 teeth and more than 120 teeth.
 7. A turbine-typevibrator as in claim 1 in which the teeth on the rotor are arranged tolay in a plane passing through the axis of the rotor.
 8. A turbine-typevibrator as in claim 1 in which the outlet and the inlet from and to therotor chamber are each connected to a pipe tap opening formed in thehousing.
 9. A turbine-type vibrator as in claim 1 in which the housingis provided with a pair of leg portions providing means for securing theassembled vibrator to a device to be vibrated.
 10. A turbine-typevibrator as in claim 1 in which a vibrator having a rotor of 1 3/8inches diameter has an inlet diameter of one hundred nine-thousandthsinch and an outlet diameter of one-quarter inch.
 11. A turbine-typevibrator as in claim 10 in which the rotor of 1 3/8 inches diameter hasits tooth profile as 48 diametral pitch or coarser.
 12. A turbine-typevibrator as in claim 1 in which a vibrator having a rotor of 1 5/8inches diameter has an inlet diameter of one hundred sixteen-thousandthsand an outlet diameter of one-quarter inch.
 13. A turbine-type vibratoras in claim 12 in which the rotor of 1 5/8 inches diameter has its toothprofile as 32 diametral pitch or coarser.
 14. A turbine-type vibrator asin claim 1 in which a vibrator having a rotor of 1 7/8 inches diameterhas an inlet diameter of one hundred sixteen-thousandths and an outletdiameter of one-quarter inch.
 15. A turbine-type vibrator as in claim 14in which the rotor of 1 7/8 inches diameter has its tooth profile as 32diametral pitch or coarser.
 16. A turbine-type vibrator as in claim 1 inwhich a vibrator having a rotor of 2 inches diameter has an inletdiameter of one hundred sixteen-thousandths and an outlet diameter offive-sixteenths inch.
 17. A turbine-type vibrator as in claim 1 in whichThe rotor of 2 inches diameter has its tooth profile as 32 diametralpitch or coarser.
 18. A turbine-type vibrator as in claim 1 in which avibrator having a rotor of 2 1/2 inches diameter has an inlet diameterof one hundred sixteen-thousandths and an outlet diameter offive-sixteenths inch.
 19. A turbine-type vibrator as in claim 18 inwhich the rotor of 2 1/2 inches diameter has its tooth profile as 32diametral pitch or coarser.
 20. A turbine-type vibrator as in claim 1 inwhich a vibrator having a rotor of 2 3/4 inches diameter has an inletdiameter of one hundred twenty-five-thousandths and an outlet diameterof three hundred ninety-six-thousandths inch.
 21. A turbine-typevibrator as in claim 20 in which the rotor of 2 3/4 inches diameter hasits tooth profile as 24 diametral pitch or coarser.
 22. A turbine-typevibrator as in claim 1 in which a vibrator having a rotor of 3 1/2inches diameter has an inlet diameter of one hundredfifty-six-thousandths and an outlet diameter of three hundred ninety-sixthousandths inch.
 23. A turbine-type vibrator as in claim 22 in whichthe rotor of 3 1/2 inches diameter has its tooth profile as 24 diametralpitch or coarser.
 24. A turbine-type vibrator as in claim 1 in which avibrator having a rotor of 5 inches diameter has an inlet diameter oftwo hundred twenty-thousandths and an outlet diameter of twenty-sevensixty-fourths inch.